Cooling system for a work vehicle

ABSTRACT

A cooling system includes a charge air cooler system that includes a first stage and a second stage. The first stage receives charge air via a charge air flow path. The first stage receives coolant fluid via a first coolant fluid flow path. The second stage receives the charge air from the first stage via the charge air flow path, such the second stage of the charge air cooler system outputs the charge air and receives the coolant fluid via a second coolant fluid flow path. The cooling system includes a low temperature radiator system that includes a low-temperature radiator that directs the coolant fluid toward the second coolant fluid flow path and a third coolant fluid flow path. The cooling system includes a high temperature radiator system that directs the coolant fluid toward the first stage via the first coolant fluid flow path.

BACKGROUND

The present disclosure relates generally to a cooling system for a workvehicle.

Certain work vehicles (e.g., tractors, harvesters, skid steers, etc.)may be used to tow or support tools to plow a field, till land, excavatesoil, harvest crops, or accomplish other ground-working operations. Theoperations performed by the work vehicle may cause internal componentsof the work vehicle to generate heat. Typical work vehicles employ acooling system to cool certain internal components. Generally, as thepower of the work vehicle increases, more cooling is used, but theoverall size of the work vehicle may not increase. As a result, theremay not be enough room (e.g., inside the work vehicle under the hood) toaccommodate typical cooling systems capable of providing suitablecooling for high-power work vehicles.

BRIEF DESCRIPTION

In one embodiment, a cooling system includes a charge air cooler systemthat includes a first stage that receives charge air at a firsttemperature via a charge air flow path, such that the first stage of thecharge air cooler system receives coolant fluid via a first coolantfluid flow path. The charge air cooler system also includes a secondstage that receives the charge air at a second temperature from thefirst stage of the charge air cooler system via the charge air flowpath, such that the second stage of the charge air cooler system outputsthe charge air at a third temperature and receives the coolant fluid viaa second coolant fluid flow path. The second temperature is lower thanthe first temperature and the third temperature is lower than the secondtemperature. In addition, the cooling system includes a low temperatureradiator system that includes a low temperature radiator that directsthe coolant fluid toward the second coolant fluid flow path and a thirdcoolant fluid flow path. The cooling system also includes a hightemperature radiator system that directs the coolant fluid toward thefirst stage of the charge air cooler system via the first coolant fluidflow path.

In another embodiment, a cooling system is provided. The cooling systemincludes a high temperature radiator system that directs the coolantfluid via a first coolant fluid flow path. The cooling system alsoincludes a water hydraulic oil cooler system that receives hydraulic oilvia a hydraulic oil flow path and receives coolant fluid via a secondcoolant fluid flow path. In addition, the cooling system includes a lowtemperature radiator system that includes a low temperature radiatorthat directs the coolant fluid toward the second coolant fluid flow pathand a third coolant fluid flow path.

In an additional embodiment, a cooling system for a work vehicle isprovided. The cooling system includes a charge air cooler system thatincludes a first stage that receives charge air at a first temperaturefrom a turbo of the work vehicle via a charge air flow path, such thatthe first stage of the charge air cooler system receives coolant fluidvia a first coolant fluid flow path. The charge air cooler system alsoincludes a second stage that receives the charge air at a secondtemperature from the first stage of the charge air cooler system via thecharge air flow path, such that the second stage of the charge aircooler system outputs the charge air at a third temperature, such thatthe second stage of the charge air cooler system receives the coolantfluid via a second coolant fluid flow path. In addition, the coolingsystem includes a low temperature radiator system that includes a lowtemperature radiator that directs the coolant fluid toward the secondcoolant fluid flow path and a third coolant fluid flow path.Furthermore, the cooling system includes a high temperature radiatorsystem that includes an engine radiator that directs coolant fluid to anengine of the work vehicle, a high temperature charge air coolerradiator that directs the coolant fluid toward the low temperatureradiator via a fourth coolant fluid flow path, and a high temperaturehydraulic oil cooler radiator that directs the coolant fluid toward thefirst stage of the charge air cooler system via the first coolant fluidflow path.

DRAWINGS

These and other features, aspects, and advantages of the presentdisclosure will become better understood when the following detaileddescription is read with reference to the accompanying drawings in whichlike characters represent like parts throughout the drawings, wherein:

FIG. 1 is a perspective view of an embodiment of a work vehicle;

FIG. 2 is a perspective view of an embodiment of a radiator assembly ofa cooling system that may be employed within the work vehicle of FIG. 1;

FIG. 3 is a block diagram of an embodiment of a cooling system that maybe employed within the work vehicle of FIG. 1; and

FIG. 4 is a block diagram of another embodiment of a cooling system thatmay be employed within the work vehicle of FIG. 1.

DETAILED DESCRIPTION

Turning to the drawings, FIG. 1 is a perspective view of an embodimentof a work vehicle 10 that may include a cooling system. In theillustrated embodiment, the work vehicle 10 is a tractor. However, itshould be appreciated that the cooling system disclosed herein may beutilized on other work vehicles, such as but not limited to buses, cars,on-road trucks, skid steers, harvesters, and construction equipment. Inthe illustrated embodiment, the work vehicle 10 includes a cab 12 and achassis 14. In certain embodiments, the chassis 14 may house a motor(e.g., diesel engine, etc.), a hydraulic system (e.g., including a pump,valves, reservoir, etc.), and other components (e.g., an electricalsystem, a suspension system, etc.) that facilitate operation of the workvehicle. In addition, the chassis 14 may support the cooling systemdescribed herein. In some embodiments, the work vehicle 10 includes ahood 15 configured to be lifted or pivotally rotated to facilitateaccess to the cooling system and/or other components of the work vehicle10.

In addition, the chassis 14 supports the cab 12 and wheels 16. Thewheels 16 may rotate in a circumferential direction to cause the forwardlinear movement of the work vehicle 10 along a direction of travel 22.In the illustrated embodiment, a coordinate system includes alongitudinal axis 24 (e.g., parallel to the direction of travel 22), alateral axis 26, and a vertical axis 28. While the illustrated workvehicle 10 includes wheels 16, in alternative embodiments, the workvehicle may include tracks or a combination of wheels and tracks thatcause the work vehicle to advance along the direction of travel 22.

The cab 12 may house an operator of the work vehicle 10. Accordingly,various controls, such as the illustrated hand controller 30, arepositioned within the cab 12 to facilitate operator control of the workvehicle 10. For example, the controls may enable the operator to controlrotational speed of the wheels 16, thereby facilitating adjustment ofthe speed and/or the direction of the work vehicle 10. In theillustrated embodiment, the cab 12 also includes a door 32 to facilitateingress and egress of the operator from the cab 12.

FIG. 2 is a perspective view of an embodiment of a radiator assembly 40of a cooling system that may be employed within the work vehicle 10 ofFIG. 1. In the illustrated embodiment, the cooling system includes tworadiator systems. As illustrated, the cooling system includes a lowtemperature radiator system 42 and a high temperature radiator system44. The cooling system also includes a fan 46 (e.g., a solid fan, aclutch fan, a flex fan, an electric fan, etc.) configured to drive air48 (e.g., external airflow) through the low temperature radiator system42 and the high temperature radiator system 44. Furthermore, the fan 46may be configured to operate at any suitable speed (e.g., about 2180revolutions per minute (RPM), etc.). Although in the illustratedembodiment the cooling system includes one fan 46 and two radiatorsystems, it should be noted that in alternative embodiments, the coolingsystem may include any other suitable number of fans and/or radiatorsystems. In some embodiments, the fan 46 may be omitted.

Furthermore, the radiator assembly 40 may have any suitable dimensionsthe enable cooling system to be supported by the chassis of the workvehicle. For example, the cooling system may have any suitable length(e.g., extended along the longitudinal axis 24), any suitable width(e.g., extended along the lateral axis 26), and any suitable height(e.g., extended along the vertical axis 28). In addition, the coolingsystem has dimensions that enable the cooling system to be housed insidethe work vehicle. For example, the cooling system may be positioned atthe front of the work vehicle and housed inside the hood. It should benoted that the dimensions of the cooling system may be modified to beincorporated into other vehicles of varying sizes. For example, asmaller fan (e.g., operated at a higher speed) may be substituted forthe illustrated fan 46 to facilitate incorporating the cooling systeminto a vehicle. The cooling system described herein provides moreefficient cooling to the various components of the work vehicle, ascompared to previous cooling systems, thereby enabling the coolingsystem to effectively cool higher power engines while being able to fitinside the work vehicle (e.g., under the hood). That is, the coolingsystem is configured to fit inside (e.g., the space constraints underthe hood of) previous/current work vehicles, while providing suitablecooling components that utilize more cooling capacity (e.g., due tohigher power requirements).

In the illustrated embodiment, the low temperature radiator system 42 ispositioned forward of the high temperature radiator system 44 and thefan 46 along the longitudinal axis 24. Accordingly, the high temperatureradiator system 44 is positioned between the fan 46 and the lowtemperature radiator system 42 along the longitudinal axis 24, such thatthe low temperature radiator system 42 is positioned forward of the hightemperature radiator system 44 relative to the direction of travel 22,and the fan is positioned reward of the high temperature radiator system44 relative the direction of travel 22. The fan is configured to directthe flow of air 48 along the longitudinal axis 24, such that the air 48flows through the high temperature radiator system 44 after the air 48flows through the low temperature radiator system 42. As such, the lowtemperature radiator system 42 may receive the cooler air (e.g., toenable the coolant to be cooled to a lower temperature). It should benoted that in additional embodiments, the fan 46 and the two radiatorsystems 42, 44 may be arranged in another suitable order along thelongitudinal axis 24. For example, the low temperature radiator system42 may be positioned behind the fan 46 or the high temperature radiatorsystem 44 relative to the direction of travel 22. In furtherembodiments, the low temperature radiator system 42, the hightemperature radiator system 44, and the fan 46 may be oriented inanother suitable direction. For example, the low temperature radiatorsystem 42, the high temperature radiator system 44, and the fan may eachbe oriented substantially along the lateral axis 26, the vertical axis28, or any other suitable direction.

The two radiator systems 42, 44 are configured to circulate coolantfluid used to cool various components of the work vehicle 10 asdiscussed in detail below. For example, the coolant fluid may includeonly water, a mixture of about 50 percent water and about 50 percentethylene glycol, only ethylene glycol, or any other suitable coolantfluid. In some embodiments, the coolant fluid may flow into the hightemperature radiator system 44 via a first opening 50. In addition, thecoolant fluid may flow out of the low temperature radiator system 42 viaa second opening 52. In further embodiments, the coolant fluid may enterthe low temperature radiator system 42 via the second opening, and thecoolant fluid may exit the high temperature radiator system 44 via thefirst opening 50. In some embodiments, the cooling system may includehas one or more stages of water cooling. For example, he first stage ofthe water cooling may be performed by the coolant connected to the hightemperature radiator and second or third stages of the water cooling maybe performed by the coolant connected to the low temperature radiatorcoolant.

FIG. 3 is a block diagram of an embodiment of a cooling system 60 thatmay be employed within the work vehicle of FIG. 1. To facilitatediscussion, the embodiments discussed herein include specific values fordimensions, heat dissipation, inlet temperature, outlet temperature, andthe like, but it should be appreciated that these specific values aremeant to be exemplary and in no way limiting. Furthermore, theembodiments discussed herein include a discussion of various flow path(e.g., fluid connections). The flow paths (e.g., fluid connections) mayinclude multiple segments fluidly coupling two components of the coolingsystem. Furthermore, the segments are each configured to direct coolantfluid. In some embodiments, the segments are configured to directcoolant fluid with no intervening components between the illustratedcomponents. For example, each illustrated segment of each illustratedcoolant fluid flow path may include a first end and a second endconfigured to form a direct fluid connection (e.g., via an annularconduit) between two components. However, in alternative embodiments,intervening components may be present between the two illustratedcomponents.

In the illustrated embodiment, the cooling system 60 includes the hightemperature radiator system 44, which includes three separate heatexchangers (e.g., radiators). In the illustrated embodiment, the hightemperature radiator system 44 includes an engine radiator 62, a chargeair cooler high temperature radiator (CAC HT radiator) 64, and ahydraulic oil cooler high temperature radiator (HOC HT radiator) 66.However, in other embodiments, the high temperature radiator system 44may include any suitable number of heat exchangers, such as one, two,four, six, etc.

In some embodiments, the engine radiator 62 is configured to dissipateabout 149 kilowatts (kW) of heat (e.g., to the environment). However, itshould be appreciated that in further embodiments, the engine radiator62 may be configured to dissipate any suitable amount of heat (e.g.,between 100 kW and 200 kW). In some embodiments, the engine radiator 62may have dimensions (e.g., width and height) of about 532 millimeters(mm) by about 825 mm, but it should be appreciated that in furtherembodiments, the engine radiator 62 may be sized to have any suitabledimensions. In addition, the engine radiator 62 outputs coolant fluid ata target temperature, such as about 94 degrees Celsius (° C.), andreceives coolant fluid via an engine radiator coolant fluid flow path 70at another temperature from an associated engine 72 (e.g., about 102°C.).

In the illustrated embodiment, the engine radiator coolant fluid flowpath 70 is a single closed-loop coolant fluid flow path, such that thecoolant fluid output from the engine radiator 62 is provided to theengine 72, and the coolant fluid output by the engine 72 is provided tothe engine radiator 62. The flow of the coolant fluid via the engineradiator coolant fluid flow path 70 may be driven by an engine pump 74configured to drive the flow of the coolant fluid at a volumetric flowrate of about 300 liters per minute (LMP), for example. In someembodiments, while the coolant fluid is flowing through the engineradiator coolant fluid flow path 70, the temperature of the air 48leaving the engine radiator 62 may be between 40° C. and 60° C. (e.g.,48° C.).

With regard to the discussion above of segments of the flow paths, inthe illustrated embodiment, the engine radiator coolant fluid flow path70 includes two segments. In particular, in the illustrated embodiment,a first segment is included between the outlet of the engine radiator 62and the inlet of the engine 72, and a second segment is included betweenthe outlet of the engine 72 and the inlet of the engine radiator 62. Asmentioned above, each illustrated segment of each illustrated flow pathmay include a first end and a second end configured to form a directfluid connection (e.g., via an annular conduit) between two components.However, in alternative embodiments, intervening components may bepresent between the two illustrated components. For example, inalternative embodiments, an intervening component may be present betweenthe outlet of the engine 72 and the inlet of the engine radiator 62along the second segment.

In some embodiments, the engine 72 may be any suitable engine forconverting fuel into mechanical energy to drive the motion of the workvehicle 10 (e.g., and/or perform other operations). For example, theengine 72 may be an internal combustion engine, such as a spark ignitionengine (e.g., gasoline engine, etc.) or a compression ignition engine(e.g., a diesel engine, a partially premixed combustion (PPC) engine, ahomogeneous charge compression ignition (HCCI) engine, etc.).Furthermore, the engine pump 74 may be any suitable pump for deliveringcoolant fluid at a target flow rate (e.g., about 300 LPM). In someembodiments, the engine pump 74 may be electrically driven or drivendirectly by the engine 72. For example, the engine pump 74 may be acentrifugal pump, an axial pump, a mixed-flow pump, a positivedisplacement pump, and the like.

Turning to the CAC HT radiator 64, in some embodiments, the CAC HTradiator 64 is configured to dissipate about 51 kW of heat (e.g., to theenvironment). However, it should be appreciated that in furtherembodiments, the CAC HT radiator 64 may be configured to dissipate anysuitable amount of heat (e.g., between 25 kW and 100 kW). In someembodiments, the CAC HT radiator 64 may have dimensions (e.g., width andheight) of about 120 mm by about 825 mm, but it should be appreciatedthat in further embodiments, the CAC HT radiator 64 may have anysuitable dimensions. Furthermore, in the illustrated embodiment, the CACHT radiator 64 is configured to output coolant toward a first stagewater charge air cooler (WCAC) 78 of a charge air cooler system 79 via aCAC HT coolant fluid flow path 80 (e.g., first coolant fluid flow path).In some embodiments, the charge air cooler system 79 may include anysuitable number of stages, such as one, two, three, four, or any othersuitable number of cooling stages. The coolant fluid that exits the CACHT radiator 64 via the CAC HT coolant fluid flow path 80 is expelled ata lower temperature than the temperature of the coolant entering the CACHT radiator 64 (e.g., because the CAC HT 64 radiator facilitates heattransfer from the coolant fluid to the environment). For example, thetemperature of the coolant fluid output by the CAC HT radiator 64 may beabout 108° C., and the temperature of the coolant fluid input to the CACHT radiator 64 may be about 113° C.

In the illustrated embodiment, the CAC HT coolant fluid flow path 80 isa single closed-loop flow path, such that the coolant fluid output fromthe CAC HT radiator 64 flows to the first stage WCAC 78, and the coolantfluid output from the first stage WCAC 78 flows to the CAC HT radiator64. The flow of the coolant fluid via the CAC HT coolant fluid flow path80 may be driven by a CAC pump 82 configured to drive the flow of thecoolant fluid in the CAC HT coolant fluid flow path 80 at a volumetricflow rate of about 160 LPM. In some embodiments, while the coolant fluidis flowing to the first stage WCAC 78, the temperature of the charge air84 output from the first stage WCAC 78 may be about 108° C.

In certain embodiments, the charge air 84 entering the first stage WCAC78 via a charge air flow path 85 may have a mass flow rate of about 1415kilograms per hour (kg/h) and a temperature of about 234° C. However, itshould he understood that the temperature and mass flow rate of thecharge air 84 depends on the type of turbocharger, the type of engineassociated with the work vehicle engine load, and boost pressure, amongother factors. In some embodiments, the first stage WCAC 78 maydissipate about 51 kW of heat. For example, the fluid coolant flowingthrough the first stage WCAC 78 may facilitate the heat dissipation ofabout 51 kW, however it should be understood that the first stage WCAC78 may dissipate any suitable amount of heat (e.g., between 25 kW and100 kW). In some embodiments, after the first stage WCAC 78 dissipatesabout 51 kW of heat, the charge air 84 may exit the first stage WCAC 78via the charge air flow path 85 at a lower temperature than when itentered the first stage WCAC 78. For example, the charge air 84 may beoutput from the first stage WCAC at about 108° C.

In the illustrated embodiment, the charge air 84 then flows from thefirst stage WCAC 78 into a second stage WCAC 86 of the charge air coolersystem 79 via the charge air flow path 85 for additional cooling. Thesecond stage WCAC 86 may dissipate about 17 kW of heat, as described indetail below, such that the charge air 84 output by the second stageWCAC 86 is about 70° C. In the illustrated embodiment, the charge air 84expelled from the second stage WCAC 86 has a temperature of about 67°C., but it should be appreciated that in additional embodiments, thecharge air may he expelled from the second stage WCAC 86 at any suitabletemperature below about 70° C., for example, such as 69.5° C., 68° C.,65° C., and the like.

Turning to the HOC HT radiator 66, in some embodiments, the HOC HTradiator 66 is configured to dissipate about 20 kW of heat (e.g., to theenvironment). However, it should be appreciated that in furtherembodiments, the HOC HT radiator 66 may be configured to dissipate anysuitable amount of heat (e.g., between 15 kW and 40 kW). In someembodiments, the HOC HT radiator 66 may have dimensions (e.g., width andheight) of about 81 mm by about 825 mm, but it should be appreciatedthat in further embodiments, the HOC HT radiator 66 have any suitabledimensions. Furthermore, in some embodiments, the HOC HT radiator 66 isconfigured to output coolant fluid toward the low temperature radiatorsystem 42 via the HOC HT coolant fluid flow path 90. In someembodiments, the coolant fluid output by the HOC HT radiator 66 has alower temperature than the coolant fluid input into the HOC HT radiator66. For example, the coolant fluid expelled by the HOC HT 66 radiatormay be at a temperature of about 72° C., while the coolant fluidentering the HOC HI radiator 66 may be at a temperature of about 74° C.,but it should be appreciated that in alternative embodiments thetemperatures at the inlet and outlet of the HOC HT radiator 66 may beany suitable temperatures. In the illustrated embodiment, the flow ofthe coolant fluid via a HOC HT coolant fluid flow path 90 (e.g., thefourth coolant fluid flow path) is driven by the HOC pump 92, which mayinclude any suitable pump configured to drive the flow of the coolantfluid into the low temperature radiator system 42 at a target volumetricflow rate. In particular, the HOC pump 92 may pump the coolant fluidinto the low temperature radiator system 42 at a volumetric flow rate ofabout 160 LMP and at a temperature of about 71° C.

In the illustrated embodiment, the low temperature radiator system 42includes a low temperature (LT) radiator 94 and an ultra-low temperature(ULT) radiator 96. As mentioned above, in some embodiments, the coolantfluid may be pumped into the low temperature radiator 94 (e.g., via theHOC HT coolant fluid flow path 90) by the HOC pump 92 at a volumetricflow of about 160 LPM. The coolant fluid may then flow from the lowtemperature radiator 94 to into the ultra-low temperature radiator 96.

In some embodiments, the low temperature radiator 94 is configured todissipate about 47 kW of heat (e.g., to the environment). However, itshould be appreciated that in further embodiments, the low temperatureradiator 94 may be configured to dissipate any suitable amount of heat(e.g., between 30 kW and 60 kW). In some embodiments, the lowtemperature radiator 94 may have dimensions (e.g., width and height) ofabout 406 mm by about 800 mm, but it should be appreciated that infurther embodiments, the low temperature radiator 94 have any suitabledimensions. In addition, the low temperature radiator 94 outputs coolantfluid at a target temperature, such as about 67° C.

In the illustrated embodiment, the coolant fluid output by the lowtemperature radiator 94 is split into two coolant fluid flow paths. Asillustrated, the coolant fluid output by the low temperature radiator 94may flow into a first low temperature radiator coolant fluid flow path100 (e.g., third coolant fluid flow path) and a second low temperatureradiator coolant fluid flow path 102 (e.g., fourth coolant fluid flowpath). The first low temperature radiator coolant fluid flow path 100may direct the coolant fluid into the ultra-low temperature radiator 96.The second low temperature radiator coolant fluid flow path 102 maydirect the flow of the coolant fluid into the second stage WCAC 86.Accordingly, in the illustrated embodiment, the fluid directed into thelow temperature radiator 94 at about 160 LPM, for example, is output tothe first low temperature radiator path 100 and to the second lowtemperature radiator coolant fluid flow path 102. The coolant fluid mayflow along the first low temperature radiator coolant fluid flow path100 and the second low temperature radiator coolant fluid flow path 102at any suitable respective volumetric flow rates. For example, the firstlow temperature radiator coolant fluid flow path 100 may receive coolantfluid at about 145 LPM, and second low temperature radiator coolantfluid flow path 102 may receive coolant fluid at about 15 LPM.

With regard to the coolant fluid directed to the first low temperatureradiator coolant fluid flow path 100, the coolant fluid is directed tothe ultra-low temperature radiator 96 (e.g., at about 15 LPM). In someembodiments, the ultra-low temperature radiator 96 is configured todissipate about 7 kW of heat (e.g., to the environment). However, itshould be appreciated that in further embodiments, the ultra-lowtemperature radiator 96 may be configured to dissipate any suitableamount of heat (e.g., between 2 kW and 20 kW). In some embodiments, theultra-low temperature radiator 96 has dimensions (e.g., width andheight) of about 101 mm by about 800 mm, but it should be appreciatedthat in further embodiments, the ultra-low temperature radiator 96 mayhave any suitable dimensions. In addition, in the illustratedembodiment, the ultra-low temperature radiator 96 outputs coolant fluidat a target temperature, such as about 59° C.

In some embodiments, the coolant fluid output by the ultra-lowtemperature radiator 96 may be directed via the first low temperatureradiator coolant fluid flow path 100 toward other components associatedwith the work vehicle 10. For example, in the illustrated embodiment,the coolant fluid output by the ultra-low temperature radiator 96 isdirected toward a condenser 106 and then toward a fuel cooler 108 beforeflowing into the HOC HT coolant fluid flow path 90 (e.g., to be directedinto the low temperature radiator 94 by the HOC pump 92). In theillustrated embodiment, the condenser 106 and the fuel cooler 108dissipate about 9 kW and about 2 kW of heat, respectively. The condensermay be any suitable device used to condense a substance from a gaseousstate to a liquid state (e.g., by cooling it), and the fuel cooler maybe any suitable device used to decrease the temperature of fuel flowinginside the work vehicle 10 (e.g., to the engine 72). Furthermore, insome embodiments, the condenser 106 and the fuel cooler 108 may be partof the heating, ventilation, and air conditioning (HVAC) system of thework vehicle. In other embodiments, the condenser 106 and the fuelcooler 108 may be replaced with any other suitable devices, such as anexpansion valve, a compressor pump, any devices associated with the airconditioning system of the work vehicle 10, etc. Furthermore, in certainembodiments, the condenser 106 or the fuel cooler 108 may be omittedand/or another component may be fluidly coupled to the first lowtemperature radiator coolant fluid flow path to receive the coolantfluid.

With regard to the coolant fluid directed to the second low temperatureradiator coolant fluid flow path 102, the coolant fluid is output by thelow temperature radiator 94 at a target temperature (e.g., about 67°C.), such that the coolant fluid is directed toward the second stageWCAC 86 (e.g., at about 145 LPM). As mentioned above, the second stageWCAC 86 may dissipate about 17 kW of heat thereby expelling the chargeair 84 (e.g., to the engine 72) at a target temperature (e.g., belowabout 70° C.). However, the second stage WCAC 86 may dissipate any othersuitable amount of heat (e.g., between 10 kW and 25 kW) based on theproperties of the second stage WCAC 86 (e.g., the number of fins, thesize of the fins, the number of coolant fluid passes, the material,etc.). The second stage WCAC 86 may output the coolant fluid toward asecond stage water hydraulic oil cooler (WHOC) 110.

In the illustrated embodiment, hydraulic oil 112 (e.g., hydraulic fluid)is directed into a first stage WHOC 114 of a WHOC system 113 via ahydraulic oil flow path 115. The hydraulic oil 112 is then directed fromthe first stage WHOC 114 into the second stage WHOC 110 of the WHOCsystem 113 in the hydraulic oil flow path 115. Indeed, the hydraulic oil112 is directed through two stages of the WHOC system 113 via thehydraulic oil flow path 115, whereby the hydraulic oil 112 is cooled byeach stage WHOC. For example, the first stage WHOC 114 and the secondstage WHOC 110 may be configured to dissipate about 31 kW and about 17kW of heat, respectively, to facilitate cooling the hydraulic oil 112.However, it should be appreciated that the cooling system 60 may includeany suitable number of stages associated with the WHOC (e.g., one stage,two stages, three stages, four stages, etc.) to cool the hydraulic oil112 (e.g., with the coolant fluid received from the low temperatureradiator 94 via the second low temperature radiator coolant fluid flowpath 102). The hydraulic oil 112 may enter the first stage WHOC 114 at avolumetric flow rate of about 92 LPM and a temperature of about 87° C.,but it should be appreciated that the hydraulic oil 112 may enter thefirst stage WHOC at any other suitable volumetric flow rate andtemperature. In addition, the second stage WHOC 110 receives thehydraulic oil 112 before outputting the hydraulic oil 112 (e.g., towardthe hydraulic system of the work vehicle 10). In some embodiments, thesecond stage WHOC 110 may output the hydraulic oil 112 at a temperaturelower than the temperature at which the hydraulic oil 112 enters thefirst stage WHOC 114. For example, the first stage WHOC 114 may receivethe hydraulic oil 112 at a temperature of about 87° C., and the secondstage WHOC 110 may output the hydraulic oil 112 at a temperature ofabout 73° C.

In some embodiments, the first stage WHOC 114 may direct the coolantfluid via the second low temperature radiator coolant fluid flow path102 toward the HOC HT radiator 66. The temperature of the coolant fluidoutput by the first stage WHOC 114 to the HOC HT radiator 66 may be at ahigher temperature (e.g., 74° C.) than the temperature of the coolantfluid received by the second stage WCAC 86 (e.g., 67° C.). As such, insome embodiments, the coolant fluid flowing via the second lowtemperature radiator coolant fluid flow path 102 is directed toward theHOC HT coolant fluid flow path 90, such that the HOC HT radiator 66cools the coolant fluid. Furthermore, coolant fluid may flow from theHOC HT radiator 66 toward the low temperature radiator system 42 via theHOC HT coolant fluid flow path 90, which also receives coolant fluidflowing from the condenser 106 and fuel cooler 108.

Accordingly, the cooling system 60 includes a high temperature radiatorsystem 44 that is configured to output coolant to the engine 72, thefirst stage WCAC 78, and the low temperature radiator system 42 viathree different heat exchangers (e.g., the engine radiator 62, the CACHT radiator 64, and the HOC HT radiator 66) of the high temperatureradiator system 44. As such, in some embodiments, the high temperatureradiator system 44 may cool (e.g., with output coolant fluid) the engine72, the charge air 84, and the coolant fluid provided to the lowtemperature radiator system 42. It should be appreciated that the hightemperature radiator system 44 may include any other suitable number ofheat exchangers (e.g., one, two, four, etc.). In addition, the coolingsystem 60 includes a low temperature radiator system 42 that isconfigured to output coolant fluid toward the second stage WCAC 86, andthe first and second stage WHOC. Furthermore, the low temperatureradiator system 42 is configured to output coolant fluid toward thecondenser 106 and the fuel cooler 108 (e.g., via the first lowtemperature coolant fluid flow path 100). As such, in some embodiments,the low temperature radiator system 42 may cool (e.g., with outputcoolant fluid) the condenser 106 and the fuel cooler 108 via the firstlow temperature radiator coolant fluid flow path 100. In addition, thelow temperature radiator system 42 may cool the charge air 84 and thehydraulic oil 112 via the second low temperature radiator coolant fluidflow path 102.

FIG. 4 is a block diagram of another embodiment of a cooling system 118that may employed within the work vehicle of FIG. 1. As illustrated, thesecond cooling system 118 has a similar configuration to that of thecooling system 60 disclosed above with reference to FIG. 3. Indeed, thesecond cooling system 118 includes the high temperature radiator system44, the low temperature radiator system 42, and the water charge aircooler system 79. In the illustrated embodiment, the cooling system 118includes a one-stage WHOC 120 (e.g., as compared to the two-stage WHOCdisclosed above with reference to FIG. 3).

In some embodiments, the one-stage WHOC 120 may be configured todissipate about 47 kW of heat. As such, the one-stage WHOC 120 mayreceive hydraulic oil 112 via the hydraulic oil flow path 115 and outputthe hydraulic oil 112 at a lower temperature (e.g., toward the hydraulicsystem associated with the work vehicle 10). For example, the one-stageWHOC 120 may receive hydraulic oil 112 via the hydraulic oil flow path115 at an inlet temperature of about 87° C. and at a volumetric flowrate of about 92 LPM, and the WHOC 120 may output the hydraulic oil 112at an outlet temperature of about 73° C. and at a volumetric flow rateof about 92 LPM.

However, it should be appreciated that the second cooling system 118 mayinclude a WHOC with any suitable number of stages (e.g., one stage, twostages, three stages, four stages, etc.) to cool the hydraulic oil 112(e.g., with the coolant fluid received from the low temperature radiator94 via the second low temperature radiator coolant fluid flow path 102).In further embodiments, the hydraulic oil 112 may enter the WHOC at anysuitable volumetric flow rate and temperature. In addition, theone-stage WHOC 120 may receive the hydraulic oil 112 before outputtingthe hydraulic oil 112 (e.g., toward the hydraulic system of the workvehicle 10).

In some embodiments, the one-stage WHOC 120 may direct the coolant fluidvia the second low temperature radiator coolant fluid flow path 102toward the HOC HT radiator 66. The temperature of the coolant fluidoutput by the one-stage WHOC 120 may he at a higher temperature (e.g.,about 74° C.) than the temperature of the coolant fluid received by thesecond stage WCAC 86 (e.g., 67° C.). In some embodiments, the coolantfluid flowing via the second low temperature radiator coolant fluid flowpath 102 is directed toward the HOC HT coolant fluid flow path 90.

While only certain features have been illustrated and described herein,many modifications and changes will occur to those skilled in the art.It is, therefore, to be understood that the appended claims are intendedto cover all such modifications and changes as fall within the truespirit of the disclosure.

1. A cooling system, comprising: a charge air cooler system, comprising:a first stage configured to receive charge air at a first temperaturevia a charge air flow path, wherein the first stage of the charge aircooler system is configured to receive coolant fluid via a first coolantfluid flow path; a second stage configured to receive the charge air ata second temperature from the first stage of the charge air coolersystem via the charge air flow path, wherein the second stage of thecharge air cooler system is configured to output the charge air at athird temperature, wherein the second stage of the charge air coolersystem is configured to receive the coolant fluid via a second coolantfluid flow path, wherein the second temperature is lower than the firsttemperature and the third temperature is lower than the secondtemperature; a low temperature radiator system, comprising: a lowtemperature radiator configured to direct the coolant fluid toward thesecond coolant fluid flow path and a third coolant fluid flow path; anda high temperature radiator system configured to direct the coolantfluid toward the first stage of the charge air cooler system via thefirst coolant fluid flow path.
 2. The cooling system of claim 1,comprising a fan, wherein the fan is position rearward the hightemperature radiator system relative to a longitudinal axis of avehicle.
 3. The cooling system of claim 2, wherein the high temperatureradiator system is positioned rearward the low temperature radiatorsystem relative to the longitudinal axis, wherein the high temperatureradiator system is positioned between the fan and the low temperatureradiator system.
 4. The cooling system of claim 1, wherein the lowtemperature radiator system comprises an ultra-low temperature radiatorconfigured to receive coolant fluid via a third coolant fluid flow path.5. The cooling system of claim 4, wherein the ultra-low temperatureradiator is configured direct the coolant fluid toward a condenser of awork vehicle via the third coolant fluid flow path.
 6. The coolingsystem of claim 1, wherein the high temperature radiator systemcomprises: an engine radiator configured to direct coolant fluid to anengine of a work vehicle; a high temperature charge air cooler radiatorconfigured to direct the coolant fluid toward the low temperatureradiator via a fourth coolant fluid flow path; and a high temperaturehydraulic oil cooler radiator configured to direct the coolant fluidtoward the first stage of the charge air cooler system via the firstcoolant fluid flow path.
 7. The cooling system of claim 1, comprising awater hydraulic oil cooler system configured to receive coolant fluidfrom the second stage of the charge air cooler system and direct thecoolant fluid toward the high temperature radiator system.
 8. Thecooling system of claim 7, wherein the water hydraulic oil cooler systemcomprises a first stage and a second stage of the water hydraulic oilcooler system, wherein the first stage of the water hydraulic oil coolersystem is configured to receive hydraulic oil via a hydraulic oil flowpath and to direct the hydraulic oil toward the second stage of thewater hydraulic oil cooler system via the hydraulic oil flow path, andthe second stage of the water hydraulic oil cooler system is configuredto receive the hydraulic oil via the hydraulic oil flow path.
 9. Thecooling system of claim 8, wherein the second stage of the waterhydraulic oil cooler system is configured to receive the coolant fluidfrom the second stage of the charge air cooler system and to direct thecoolant fluid toward the first stage of the water hydraulic oil coolersystem, and the first stage of the water hydraulic oil cooler system isconfigured to direct the coolant fluid toward the high temperatureradiator system.
 10. The cooling system of claim 1, wherein the secondstage of the charge air cooler system is configured to output the chargeair towards an environment.
 11. The cooling system of claim 1, whereinthe third temperature is below 70° C.
 12. A cooling system, comprising:a high temperature radiator system configured to direct the coolantfluid via a first coolant fluid flow path; a water hydraulic oil coolersystem configured to receive hydraulic oil via a hydraulic oil flow pathand to receive coolant fluid via a second coolant fluid flow path; and alow temperature radiator system, comprising a low temperature radiatorconfigured to direct the coolant fluid toward the second coolant fluidflow path and a third coolant fluid flow path.
 13. The cooling system ofclaim 12, wherein the water hydraulic oil cooler system comprises afirst stage and a second stage, wherein the first stage of the waterhydraulic oil cooler system is configured to receive the hydraulic oilvia the hydraulic oil flow path and to direct the hydraulic oil towardthe second stage of the water hydraulic oil cooler system via thehydraulic oil flow path, wherein the second stage of the water hydraulicoil cooler system is configured to receive the hydraulic oil via thehydraulic oil flow path, and the second stage of the water hydraulic oilcooler system is configured to receive coolant fluid from the lowtemperature radiator system via the second coolant fluid flow path. 14.The cooling system of claim 13, wherein the second stage of the waterhydraulic oil cooler system is configured to: receive coolant fluid fromthe low temperature radiator system via the second coolant fluid flowpath; raise the temperature of the coolant fluid; and direct the coolantfluid toward the first stage of the water hydraulic oil cooler systemvia the second coolant fluid flow path.
 15. The cooling system of claim13, wherein the first stage of the water hydraulic oil cooler system isconfigured to: receive the coolant fluid from the second stage of thewater hydraulic oil cooler system via the second coolant fluid flowpath; and direct the coolant fluid toward the high temperature radiatorsystem via the second coolant fluid flow path.
 16. A cooling system fora work vehicle, comprising: a charge air cooler system, comprising: afirst stage configured to receive charge air at a first temperature froma turbo of the work vehicle via a charge air flow path, wherein thefirst stage of the charge air cooler system is configured to receivecoolant fluid via a first coolant fluid flow path; a second stageconfigured to receive the charge air at a second temperature from thefirst stage of the charge air cooler system via the charge air flowpath, wherein the second stage of the charge air cooler system isconfigured to output the charge air at a third temperature, wherein thesecond stage of the charge air cooler system is configured to receivethe coolant fluid via a second coolant fluid flow path; a lowtemperature radiator system, comprising: a low temperature radiatorconfigured to direct the coolant fluid toward the second coolant fluidflow path and a third coolant fluid flow path; and a high temperatureradiator system, comprising: an engine radiator configured to directcoolant fluid to an engine of the work vehicle; a high temperaturecharge air cooler radiator configured to direct the coolant fluid towardthe low temperature radiator via a fourth coolant fluid flow path; ahigh temperature hydraulic oil cooler radiator configured to direct thecoolant fluid toward the first stage of the charge air cooler system viathe first coolant fluid flow path.
 17. The cooling system of claim 16,wherein the first stage of the charge air cooler system is configured toreceive the charge air from a turbo of the work vehicle.
 18. The coolingsystem of claim 16, wherein the low temperature radiator systemcomprises an ultra-low temperature radiator configured to direct thecoolant fluid toward a condenser of the work vehicle via the third flowpath.
 19. The cooling system of claim 18, wherein the coolant fluid isreceived by the condenser is directed toward a fuel cooler and the thirdcoolant fluid flow path.
 20. The cooling system of claim 16, wherein thesecond stage of the charge air cooler system is configured to output thecharge air at a third temperature toward the environment.